Multiple-stage small temperature differential heat-powered pump

ABSTRACT

A pump system is disclosed for pumping a first liquid from a source to a storage facility comprising a multiple-stage small temperature differential heat-powered pump, a second liquid heater operable to heat a second liquid to a fixed hot temperature, and a third liquid cooler operable to cool a third liquid to a fixed cold temperature, wherein hot liquids and cold liquids are diverted into the multiple-stage small temperature differential heat-powered pump.

This application is a continuation of application Ser. No. 242,242,filed Mar. 10, 1981, now U.S. Pat. No. 4,347,045.

This invention relates to a heat-powered pump and more particularly to amultiple-stage small temperature differential heat-powered pump and agenerating system utilizing a plurality of multiple-stage smalltemperature differential heat-powered pumps.

Previous inventions have utilized a flexible diaphragm as the pumpingelement with a volatile liquid as a working fluid. The prior art islimited in the pressure and volume of fluid that can be pumped when avaporizable liquid is varied within set temperature limits. The use of asingle vaporizable liquid in heat-powered hydraulic pumps operatingbetween fixed temperatures limits the output pressure capability to anextent that such pumps are relegated to applications where low pressureand pumping capacities are acceptable. Many desired applications requirehigher pressure and higher flow rates, such as high-capacity irrigationsystems, pumping of water from a lower level to a higher level reservoirfor municipal-type water systems, and the powering of a large hydraulicturbine electric generator combination for the inexpensive conversion ofsolar energy into electric power. In localities lacking elevated waterstorage facilities or when electric power is needed only during daylighthours, a generating system, as disclosed herein, might be preferableutilizing a plurality of multiple-stage small temperature differentialheat-powered pumps. The present invention comprises a multiple-stagesmall temperature differential heat-powered pump which has thecapability of a high output pressure when operating between fixedtemperatures.

An object of the present invention is to provide a multiple-stage smalltemperature differential heat-powered pump operable to produce highoutput pressures utilizing fixed temperatures.

Another object of the present invention is to provide a generatingsystem utilizing a plurality of multiple-stage small temperaturedifferential heat-powered pumps.

A further object of the present invention is to place a plurality ofcontainers holding a plurality of liquids into two troughs whichalternately hold hot and cold water in order to alternately vary thepressure of the plurality of liquids to the vapor pressure for a fixedcold temperature and the vapor pressure for a fixed hot temperature.

Still another object of the present invention is to provide amultiple-stage small temperature differential heat-powered pump whereineach stage is separated by one of a plurality of check valves.

A further object of the present invention is to provide a multiple-stagesmall temperature differential heat-powered pump wherein each stage hasa pressure chamber including a flexible member containing the vapor ofone of a plurality of liquids and wherein the liquid in the flexiblemember in one stage is being subjected to a hot temperature while theliquid in the flexible member in the next stage is subjected to a coldtemperature with the temperatures in each flexible member alternating asthe pumping operates.

Another object of the present invention is to provide a multiple-stagesmall temperature differential heat-powered pump with liquid heatingmeans and liquid cooling means which enter an input water divertingmeans wherein hot water and cold water are alternately diverted into aplurality of troughs within which are containers holding a plurality ofvaporizable liquids.

Still another object of the present invention is to provide a generatorutilizing a plurality of multiple-stage small temperature differentialheat-powered pumps utilizing liquid heating means and liquid coolingmeans to provide hot and cold water to an input water diverting meanswhich diverts hot and cold water alternately into a plurality of troughswithin which are a plurality of containers holding a plurality ofvaporizable liquids.

A further object of the present invention is to provide a multiple-stagesmall temperature differential heat-powered pump and a generating systemutilizing a plurality of multiple-stage small temperature differentialheat-powered pumps which can utilize solar energy in liquid heatingmeans to provide for commercial solar power production.

These and other objects and features of the invention will be apparentfrom the following description and appended claims.

Briefly, the specification discloses a pump system for puming a firstliquid from a source to a storage facility and a generating system forconverting flow of a pressurized first liquid to electrical power. Thepump system comprises a multiple-stage small temperature differentialheat-powered pump. A second liquid heating means is operable to heat asecond liquid to a fixed hot temperature. The hot liquid is divertedinto the multiple-stage small temperatue differential heat-powered pump.A third liquid cooling means is operable to cool a third liquid to afixed cold temperature where it becomes a cold liquid. The cold liquidis divertable into the multiple-stage small temperature differentialheat-powered pump. The generating system comprises a plurality ofmultiple-stage small temperature differential heat-powered pumpsutilized along with the second liquid heating means operable to heat asecond liquid to a fixed hot temperature where it becomes a hot liquidand a third liquid cooling means operable to cool a third liquid to afixed cold temperature where it becomes a cold liquid. The hot liquidand cold liquid are divertable into a plurality of multiple-stage smalltemperature differential heat-powered pumps. A hydraulic-to-mechanicalpower conversion means is operative to convert the flow of thepressurized first liquid to mechanical power. The input of thehydraulic-to-mechanical power conversion means is connected to theoutput of the plurality of the multiple-stage small temperaturedifferential heat-powered pumps. The output of thehydraulic-to-mechanical power conversion means is connected to the inputof the plurality of multiple-stage small temperature differentialheat-powered pumps. A mechanical-to-electrical power conversion means isconnected to the hydraulic-to-mechanical power conversion means and isoperative to produce electrical power. The hot liquid may be hot waterand the cold liquid may be cold water. The second liquid heating meansmay utilize solar energy to heat the second liquid to a fixed hottemperature. The hot liquid and the cold liquid are pumped into an inputwater diverting means which controls the flow of the hot liquid and thecold liquid into the multiple-stage small temperature differentialheat-powered pump. The input water diverting means diverts the hotliquid and the cold liquid alternately into each one of a plurality oftroughs within the multiple-stage small temperature differentialheat-powered pump. Each of the plurality of multiple-stage smalltemperature differential heat-powered pumps comprises a plurality ofpumping stages and a plurality of check valves. One of the plurality ofcheck valves is located on the input and output of each multiple-stagesmall temperature differential heat-powered pump. A check valve is alsolocated between each of the plurality of pumping stages. Each of theplurality of pumping stages comprises a pressure chamber operable tohold the first liquid.

A flexible member within the pressure chamber operates, when expanded,to exert pressure against the first liquid and to force the first liquidfrom the pressure chamber through one of the plurality of check valvesbetween the pressure chamber and the next pressure chamber of the nextsubsequent pumping stage of the plurality of pumping stages or theoutput, if the pressure chamber is within the last of the plurality ofpumping stages, when the pressure within the pressure chamber exceedsthe next pressure in the next pressure chamber or the output. Theflexible member is connected to a container which is one of a pluralityof containers. Each of the plurality of containers holds one of theplurality of vaporizable liquids. When the container is subjected to hotliquid, the vaporizable liquid vaporizes causing the flexible member toexpand. When the container is subjected to cold liquid, the vaporizableliquid condenses causing the flexible member to contract.

Each one of the plurality of vaporizable liquids which vaporizes intothe flexible member has a higher vapor pressure, when heated to thefixed hot temperature, than the cold vapor pressure of the next one ofthe plurality of vaporizable liquids which vaporizes into the nextflexible member within the pressure chambers or to the output, if theflexible member is within the last of the plurality of pumping stages.

Each one of the plurality of containers is secured within one of theplurality of troughs. Each container is subjected alternately to the hotliquid and then the cold liquid. Each of the plurality of pumping stageshas a flexible member connected to one of the plurality of containers.Each one of the plurality of containers is secured within one of theplurality of troughs and is subjected alternately to hot liquid and coldliquid.

The next subsequent pumping stage of the plurality of pumping stages hasa next flexible member connected to another one of the plurality ofcontainers which is secured within another one of the plurality oftroughs and is also subjected alternately to the cold liquid and the hotliquid at times opposite to the first of the plurality of containers.When one of the plurality of containers is subjected to the hot liquid,the another one of the plurality of containers is subjected to the coldliquid and vice versa. In the plurality of pumping stages, when thefirst stage has a first flexible member connected to a first containersubject to the hot liquid, the second stage would have a second flexiblemember connected to a second container subjected to the cold liquid.Each odd-numbered container is subjected to the opposite condition ofeach even-numbered container. When the first stage has a first flexiblemember connected to the first container subjected to cold liquid, thesecond stage has a second flexible member connected to the secondcontainer subjected to the hot liquid. Each odd-numbered container issubjected to the opposite condition of each even-numbered containerwithin the plurality of containers connected to the plurality of pumpingstages.

The first vaporizable liquid in the first container, which is connectedto the first flexible member in the first pumping stage, has a coldvapor pressure lower than the pressure of the first liquid in thesource. In the generating system, the first vaporizable liquid in thefirst container, which is connected to the first flexible member in thefirst pumping stage, has a cold vapor pressure lower than the pressureof the output of the hydraulic-to-mechanical power conversion means.

The second vaporizable liquid in the second container, which isconnected to the second flexible member in the second pumping stage, hasa cold vapor pressure lower than the hot vapor pressure of the firstvaporizable liquid in the first container. When the first container issubjected to the hot liquid and when the second container is subjectedto the cold liquid, the pressure within the first pumping stage isgreater than the pressure within the second pumping stage and the firstliquid will move through the one of the plurality of check valvesbetween the first pumping stage and the second pumping stage into thesecond pumping stage.

The plurality of troughs may comprise a first trough and a secondtrough. The output water diverting means is operable to control the flowof the hot liquid from the multiple-stage small temperature differentialheat-powered pump back to the second liquid heating means and to controlthe flow of the cold liquid from the multiple-stage small temperaturedifferential heat-powered pump back to the third liquid cooling means.The input water diverting means comprises an inlet gate with a firstinlet gate position and a second inlet gate position. When the inletgate is in the first inlet gate position, the hot liquid is divertedinto the first trough and the cold liquid is diverted into the secondtrough. When the inlet gate is in the second inlet gate position, thehot liquid is diverted into the second trough and the cold liquid isdiverted into the first trough. The output water diverting meanscomprises an outlet gate with a first outlet gate position and a secondoutlet gate position. When the outlet gate is in the first outlet gateposition, the hot liquid is diverted from the first trough back to thesecond liquid heating means and the cold liquid is diverted from thesecond trough back to the third liquid cooling means. When the outletgate is in the second outlet gate position, the hot liquid is divertedfrom the second trough back to the second liquid heating means and thecold liquid is diverted from the first trough back to the third liquidcooling means. A gate control means is connected to one of the pluralityof multiple-stage small temperature differential heat-powered pumps andoperates to change the inlet gates and the outlet gates simultaneouslyfrom one gate position to another. Each of the plurality of check valvesmay comprise a plurality of hinged members. The generating system mayhave two multiple-stage small temperature differential heat-poweredpumps. In the even-numbered pumping stages for each of the twomultiple-stage small temperature differential heat-powered pumps, theeven-numbered flexible members within the even-numbered pressurechambers are connected to the even-numbered containers which are locatedin the same trough with the odd-numbered containers which are connectedto the odd-numbered flexible members within the odd-numbered pressurechambers of the other multiple-stage small temperature differentialheat-powered pump. The container for the first vaporizable liquid isconnected to the first flexible member and the container for the thirdvaporizable liquid is connected to the third flexible member in thefirst multiple-stage small temperature differential heat-powered pumpand are secured in the first trough along with the container for thesecond vaporizable liquid connected to the second flexible member in thesecond multiple-stage small temperature differential heat-powered pump.The container for the first vaporizable liquid connected to the firstflexible member and the container for the third vaporizable liquidconnected to the third flexible member in the second multiple-stagesmall temperature differential heat-powered pump are secured in thesecond trough along with the container for the second vaporizable liquidconnected to the second flexible member in the first multiple-stagesmall temperature differential heat-powered pump.

In the generating system, the first vaporizable liquid in the firstmultiple-stage small temperature differential heat-powered pump may beidentical to the first vaporizable liquid in the second multiple-stagesmall temperature differential heat-powered pump. Each numberedvaporizable liquid connected to the same numbered stage in each of thetwo multiple-stage small temperature differential heat-powered pumps isidentical for each similar stage of the two multiple-stage smalltemperature differential heat-powered pumps. Each succeeding stage, ofcourse, has a different vaporizable liquid with different pressureproperties for the fixed hot and cold temperatures.

The plurality of multiple-stage small temperature differentialheat-powered pumps may be two or a greater plurality, if desired, and ifsufficient liquid heating means and liquid cooling means are availableto support the desired plurality of multiple-stage small temperaturedifferential heat-powered pumps.

The containers utilized within each stage may be individually designedto perform as an appropriate heat exchanger to obtain the desired degreeof vaporization or condensation of the liquid enclosed within the heatexchanger. The plurality of stages of each multiple-stage smalltemperature differential heat-powered pump may be considered byterminology usage as being a first stage followed by a second stage,followed by a third stage, followed by a fourth stage, followed by afifth stage, followed by a sixth stage, etc. The first, third, and fifthstages would be considered odd-numbered stages. The second, fourth, andsixth stages would be considered even-numbered stages.

The liquid heated by the liquid heating means 123 may be water or anyother desired liquid. The liquid cooled by the liquid cooling means 125may be water or any other desired liquid.

The invention will be more fully understood from the following detaileddescription and appended claims when taken with the drawings in which:

FIG. 1 is a perspective view of a solar-powered multi-stage pumpingsystem used for filling a reservoir 126 and generating electricity.

FIG. 2 is a schematic display of the pumping sequence for heat-poweredpump system 244.

FIG. 3 is a schematic representation of heat-powered pump system 244.

FIG. 4 is a top view of heat-powered pump system 244.

FIG. 5 is a sectional view through Section 5--5 of check valve assembly13 in FIG. 4.

FIG. 6 is a partial sectional view at Section 6--6 of second trough 43in FIG. 4.

FIG. 7 is a partial sectional view at Section 7--7 of first trough 42 inFIG. 4.

FIG. 8 is an end elevational view of the discharge end of heat-poweredpump system 244.

FIG. 9 is an end elevational view of the intake end of heat-powered pumpsystem 244.

FIG. 10 is a graphic representation showing the relationship between thepounds pressure per square inch gauge and the stage utilized with aspecific vaporizable liquid and temperature applied thereto for thevarious stages in the pumping sequence.

FIG. 11 is a schematic representation of gate control means 132.

FIG. 12 is a lateral sectional view through input water diverting means147 at inlet gate 65.

FIG. 13 is a sectional view of input water diverting means 147 taken atSection 13--13 of FIG. 12.

FIG. 14 is a partial isometric view of heat collector trough 61 ofliquid heating means 123.

FIG. 15 is a sectional view of heat collector trough 61 of liquidheating means 123 taken at Section 15--15 of FIG. 14.

FIG. 16 is a cross-sectional view of cooling trough 151 which may beutilized as liquid cooling means 125.

FIG. 17 is a schematic representation of heat-powered generating system245.

FIG. 18 is a schematically represented view of heat-powered generatingsystem 245.

FIG. 19 is a graphic representation showing the relationship between thepounds pressure per square inch gauge and the stage utilized with thespecific vaporizable liquid and temperature applied thereto for variousstages in the pumping sequences within the heat-powered generatingsystem 245.

FIG. 20 is a sectional view of check valve 13 at Section 20--20 of FIG.5.

Referring now to the drawings, FIG. 1 is a perspective view of asolar-powered multi-stage pumping system used for filling a reservoir126 and generating electricity. The reservoir 126 is shown located inhigh or mountainous land 157. The multiple-stage small temperaturedifferential heat-powered pump 124 is shown located in flat land 156.Liquid heating means 123 is utilized to heat a liquid. The liquidheating means 123 shown is a trough-type solar collector utilizingtrough 61. Liquid cooling means 125, for this illustration, is the river125 which is also the source of the water taken in trough inlet pipe 70.Connecting trough 149 is the inlet trough for the cold water for thesystem. Connecting trough 148 is the outlet connecting trough carryingthe cold water from the system back to the river 125. Pipe 34 carriesthe pressurized water 35 up to the elevated storage means or reservoir126. Water supply pipe 246 supplies pressurized water to generatingstation 153. Discharge pipe 247 discharges water from generating station153 back into the cold water supply, which is the river 125. Extendingfrom generating station 153 are electrical wires 130 carryingelectricity to an electrical load 152 (not shown). FIG. 1 is merelyillustrative of one prospective possibility for utilization of theheat-powered pumping system 244 of the present invention.

FIG. 2 is a schematic display of the pumping sequence for heat-poweredpump system 244. Heat-powered pump system 244 comprises pumping stages1, 2, 3, 4, 5, and 6. Pumping stage 1 comprises a flexible member 22within a pressure chamber 16. Flexible member 22 contains a vapor 29.Pumping stage 2 comprises a flexible member 23 within pressure chamber17. Flexible member 23 contains vapor 29. Pumping stage 3 comprises aflexible member 24 within a pressure chamber 18. Flexible member 24contains a vapor 30. Pumping stage 4 comprises a flexible member 25within a pressure chamber 19. Flexible member 25 contains a vapor 31.Pumping stage 5 comprises a flexible member 26 within a pressure chamber20. Flexible member 26 contains a vapor 32. Pumping stage 6 comprises aflexible member 27 within a pressure chamber 21. Flexible member 27contains a vapor 33.

In heat-powered pump system 244, water 7 is being pumped from a watersource 127 to an elevated storage means 126. The water 7 is pumpedthrough connecting means or pipe 8 and through check valve 9 intopumping stage 1. The water 7 then passes through check valve 10 intopumping stage 2. The water 7 then passes through check valve 11 intopumping stage 3. The water 7 then passes through check valve 12 intopumping stage 4. The water 7 then passes through check valve 13 intopumping stage 5. The water 7 then passes through check valve 14 intopumping stage 6. The water 7 then passes through check valve 15 andthrough connecting means or pipe 34 to the elevated storage means 126.The water within pipe 34 becomes pressurized water 35.

Flexible member 22 contains vapor 28 from liquid "A" in container 44.Flexible member 23 contains vapor 29 from liquid "B" in container 47.Flexible member 24 contains vapor 30 from liquid "C" in container 45.Flexible member 25 contains vapor 31 from liquid "D" in container 48.Flexible member 26 contains vapor 32 from liquid "E" in container 46.Flexible member 27 contains vapor 33 from liquid "F" in container 49.

Pipe 36 with flexible section 136 connects container 44 for liquid "A"to flexible member 22. Pipe 27 connects container 45 for liquid "D" toflexible member 24. Pipe 38 connects container 46 for liquid "E" toflexible member 26. Pipe 39 connects container 47 for liquid "B" toflexible member 23. Pipe 40 connects container 48 for liquid "D" toflexible member 25. Pipe 41 connects container 49 for liquid "F" toflexible member 27.

Containers 44, 45, and 46 are in a first trough 42. Containers 47, 48,and 49 are in a second trough 43. Gate control means 132 is connected bycable 50 to container 44. Pumping stages 1, 2, 3, 4, 5, and 6 areenclosed within pump body 131.

FIG. 3 is a schematic representation of heat-powered pump system 244.Water 7 is taken from water source 127 through inlet pipe 70 which isequivalent to the connecting means or pipe 8 and into the multi-stagesmall temperature differential heat-powered pump 124. The pressurizedwater 35 flows from the multiple-stage small temperature differentialheat-powered pump 124 through pipe 34 to elevated storage means 126. Theother water flow shown in FIG. 3 is the flow of water to operate themultiple-stage small temperature differential heat-powered pump 124.

Liquid heating means 123 heats a liquid. The hot liquid flows through ahot water pump 69 with a motor speed control 128 and through connectingtrough 79 to input water diverting means 147. The input water divertingmeans 147 diverts the hot liquid into the appropriate trough, eitherfirst trough 42 or second trough 43 which extend within themultiple-stage small temperature differential heat-powered pump 124. Theheated liquid will be utilized by the multiple-stage small temperaturedifferential heat-powered pump 124 and will enter the output waterdiverting means 146. The previously hot liquid will then be returned byconnecting trough 78 to the liquid heating means 123.

Liquid cooling means 125 cools a liquid. The cold liquid flows throughthe cold water pump 68 and through connecting trough 149 to input waterdiverting means 147. The input water diverting means 147 diverts thecold liquid into the appropriate trough, either first trough 42 orsecond trough 43 which extend within the multiple-stage smalltemperature differential heat-powered pump 124. The cold liquid will beutilized by the multiple-stage small temperature differentialheat-powered pump 124 and will enter the output water diverting means146. The previously cold liquid will then be returned by connectingtrough 148 to the liquid cooling means 125. The expandable membersdiscussed herein may be flexible bladders, diaphrams, bellows, orsimilar flexible members in which vaporized liquids may exert pressurein order to expand the area inside the flexible members so that pressureis exerted against the first liquid within the container within whichthe flexible members reside.

The gate control means 132 is connected to the multiple-stage smalltemperature differential heat-powered pump 124 by wire 139 and wire 140.The gate control means 132 is connected to hot water pump 69 by wire142. The gate control means 132 is connected to cold water pump 68 bywire 141. The gate control means 132 is connected to input waterdiverting means 147 by wire 143. The gate control means 132 is connectedto output water diverting means 146 by wire 144.

The pressurized water 35 in elevated storage means 126 may be utilizedby generating station 153 to handle electrical load 152. The generatingstation 153 is connected to the electrical load 152 by wire 130. Thegenerating station 153 may comprise a low level hydraulic-to-mechanicalpower conversion means 154 and a mechanical-to-electrical powerconversion means 155.

FIG. 4 is a top view of heat-powered pump system 244. The input waterdiverting means 147 comprises inlet gate 65. The output water divertingmeans 146 comprises outlet gate 62. The inlet gate 65 can be placed intobasically two positions, inlet gate position 66 and inlet gate position67. The outlet gate 62 can be placed into basically two positions,outlet gate position 63 and outlet gate position 64. When inlet gate 65is in position 66, outlet gate 62 is in position 63. When inlet gate 65is in position 67, outlet gate 62 is in position 64.

To help explain the water path flow in FIG. 4, arrow 171 is utilized toindicate the hot water path with outlet gate 62 in position 63 and inletgate 65 in position 66. Arrow 172 indicates the cold water path withoutlet gate 62 in position 63 and inlet gate 65 in position 66. Arrow173 is utilized to indicate the hot water path with outlet gate 62 inposition 64 and inlet gate 65 in position 67. Arrow 174 is utilized toindicate the cold water path with outlet gate 62 in position 64 andinlet gate 65 in position 67.

With inlet gate 65 in position 66 and outlet gate 62 in position 63, thehot water will flow through connecting trough 79 past motor speedcontrol 128 and hot water pump 69, and through inlet gate 65 in position66 through trough section 71, and into first trough 42 within which arecontainers 44, 45, and 46. The hot water will then flow through troughsection 72 into outlet gate 62 in position 63 and then into connectingtrough 78, which will return the hot water to liquid heating means 123.The cold water will enter from liquid cooling means 125 throughconnecting trough 149, past cold water pump 68, and into inlet gate 65in position 66. The cold water will be diverted into second trough 43within which are containers 47, 48, and 49. The cold water will thenenter outlet gate 62 in position 63 and is diverted to connecting trough148 to be returned to liquid cooling means 125. When the hot water is infirst trough 42, the cold water is in second trough 43.

With inlet gate 65 in position 67 and outlet gate 62 in position 64, thehot water will flow through connecting trough 79, past motor speedcontrol 128 and hot water pump 69 and through inlet gate 65 in position67, and then into second trough 43 within which are containers 47, 48,and 49. The hot water will then flow into outlet gate 62 in position 64,and then into connecting trough 78 which will return the hot water toliquid heating means 123. The cold water will enter from liquid coolingmeans 125 through connecting trough 149, past cold water pump 68, andinto inlet gate 65 in position 67. The cold water will be diverted intotrough section 71 and then into first trough 42, within which arecontainers 44, 45, and 46. The cold water then passes into troughsection 72 and then enters outlet gate 62 in position 64 and is divertedto connecting trough 148 to be returned to liquid cooling means 125.When the cold water is in first trough 42, the hot water is in secondtrough 43.

FIG. 5 is a sectional view through Section 5--5 of check valve assembly13 in FIG. 4. Check valve 13 is a check valve assembly between pumpingstage 4 and pumping stage 5 and is shown as illustrative of a type ofcheck valve assembly that may be utilized in the present invention.

Check valve assembly 13 comprises an upper hinged member 159, a middlehinged member 160, and a lower hinged member 161. Upper hinged member159 is connected by hinges 162 and 163. Middle hinged member 160 isconnected by hinges 164 and 165. Lower hinged member 161 is connected byhinges 166 and 167. Upper hinged member 159 opens and closes upperopening 168. Middle hinged member 160 opens and closes middle opening169. Lower hinged member 161 opens and closes lower opening 170. Hingedmembers 159, 160, and 161 are of the "swinging door" variety forsimplicity and reliability and, in the open position, a minimum ofresistance is offered to the flow of water. A plurality of hingedmembers is utilized so that in the open position the hinged members donot extend into the pressure chamber sufficiently to interfere with theextended bladder. To insure that the hinged members 159, 160, and 161close automatically in the absence of a pressure differential across thechamber wall, the pump body 131 may be tilted so that the output end ishigher than the input end. Any number of hinged members desired may beutilized in each check valve assembly.

The input water diverting means 147 is an input liquid diverting means147 for any liquid that may be used. The output water diverting means148 is an output liquid diverting means 148 for any liquid that may beused.

FIG. 5 shows an example of a check valve assembly 13 which may beutilized. Any check valve assembly desirable to the user may also beutilized.

FIG. 6 is a partial sectional view at Section 6--6 of second trough 43in FIG. 4. Second trough 43 contains container 47 for liquid "B",container 48 for liquid "D", and container 49 for liquid "F". Container47 may be supported by support members 189 and 190. Container 48 may besupported by support members 191 and 192. Container 49 may be supportedby support members 193 and 194. Second trough 43 may be supported bytrough support 180 which is secured to the plain or flat land 156.Second trough 43 holds water 196 which may be hot or cold depending onthe cycle of the heat-powered pump system 244.

FIG. 7 is a partial sectional view at Section 7--7 of first trough 42 inFIG. 4. First trough 42 contains container 44 for liquid "A", container45 for liquid "C", and container 46 for liquid "E". Container 45 forliquid "C" may be supported by support members 185 and 186. Container 46for liquid "E" may be supported by support members 187 and 188.Container 44 for liquid "A" may be supported by support guide 181 onsupport rod 183 and support guide 182 on support rod 184. Cable 50 isconnected onto container 44 for use with gate control means 132.

The first trough 42 and the second trough 43 are elevated to insure thatthe water flows downward and empties out of the first trough 42 and thesecond trough 43 when the gate control means 132 causes the gates tochange positions. This elevation insures that when the cold water pump63 has stopped momentarily and the gate positions are changed, the coldwater will drain from the troughs prior to the application of hot water.This feature insures that there is no residual cold water which wouldhave to be heated by the incoming hot water. First trough 42 holds water196 which may be hot or cold depending on the cycle of the heat-poweredpump system 244.

FIG. 8 is an end elevational view of the discharge end of theheat-powered pump system 244. Connecting trough 149 connects the liquidcooling means 125 to the input water diverting means 147. Output pipe 34carries the pressurized water 35 to the elevated storage means 126.Trough support 179 supports first trough 42. Trough support 180 supportssecond trough 43. Connecting trough 79 leading from liquid heating means123 is shown carrying hot water through hot water pump 69 and into theheat-powered pump system 244. Various pipes 36, 37, 38, 39, 40, and 41carrying various liquids are shown.

FIG. 9 is an end elevational view of the intake end of heat-powered pumpsystem 244. Connecting trough 78 returning hot water from output waterdiverting means 146 to liquid heating means 123 is shown. Trough section72 connects to first trough 42 and to outlet gate 62 (not shown). Pumpbody 131 connects to pipes 36, 37, 38, 39, 40, and 41 holding variousvaporized liquids extending to either first trough 42 or second trough43. Pipes 36, 37, and 38 extend to first trough 42. Pipes 39, 40, and 41extend to second trough 43. Connecting means or pipe 8 brings water 7from water source 127 (not shown) into the pump body 131.

FIG. 10 is a graphic representation showing the relationship between thepounds pressure per square inch gauge and the stage utilized with aspecific vaporizable liquid and temperature applied thereto for thevarious stages in the pumping sequence.

As shown previously in FIG. 2 and FIG. 4, the various pumping sectionseach contain a pressure chamber within which is a flexible member. Eachflexible member is connected to a different liquid within a differentcontainer in one of two troughs. When the trough in which a container isplaced is supplied with hot water, the liquid in the container tends tovaporize. The vapor is carried through a pipe into the flexible member.The flexible member expands as the volume of vaporized liquid increases.The flexible member may expand to such an extent as to virtually fillthe pressure chamber within which it is located. The pressure, that isapplied by the expanding flexible member against the liquid that isalready in the pressure chamber, forces that liquid against the checkvalves located on each side of the pressure chamber. As the pressurewithin the pressure chamber is greater than the pressure in the nexthighest numbered pressure chamber, then the liquid within the pressurechamber will be forced through the check valve into the next highestnumbered pressure chamber. As can be seen clearly in FIG. 2, the presentsystem operates by having the flexible member deflated in one chamber,while being inflated in the next thereby pushing or pumping the liquidthrough the pump body 131 toward the elevated storage means 126.

As an example as seen in FIG. 2, liquids "A", "C", and "E" are in thefirst trough 42 and, when that trough contains cold water, the liquidsare condensed and the flexible members in pumping stages 1, 3, and 5 aredeflated. Liquids "B", "D", and "F" in second trough 43 have hot waterwhich is vaporizing those liquids and causing the flexible members inpumping stages 2, 4, and 6 to be inflated. The inflated flexible member23 in pumping stage 2 would force liquid through check valve 11 intopumping stage 3. The inflated flexible member 25 in pumping stage 4would force liquid through check valve 13 into pumping stage 5. Theinflated flexible member 27 in pumping stage 6 would force liquidthrough check valve 15 into pipe 34 where the pressurized water 35 willbe carried to the elevated storage means 126.

In the alternative, if the cold water was removed from the first trough42 and hot water placed in first trough 42, while at the same time thehot water was removed from second trough 43 and cold water placedtherein, the flexible members in the pumping stages would be in theopposite condition. The flexible members in pumping stages 1, 3, and 5would be inflated and would force liquid through the next check valve tothe following stage. The flexible members in pumping stages 2, 4, and 6would be deflated and those stages would be filled with liquid from theprior stages.

FIG. 10 shows a graphic representation of the relationship between thepressure produced into the various stages. FIG. 10 assumes a situationwhere the cold water temperature is 70° F. and the hot water temperatureis 130° F. and assumes the following to be approximately accurate: at70° F. the pounds pressure exerted by "Freon 113" vapor is -9.7P.S.I.G.; at 130° F. the pounds pressure exerted by "Freon 113" vapor is4 P.S.I.G.; at 70° F. the pounds pressure exerted by "Freon 11" vapor is0 P.S.I.G.; at 130° F. the pounds pressure exerted by "Freon 11" vaporis 28 P.S.I.G.; at 70° F. the pounds pressure exerted by "Freon 21"vapor is 10 P.S.I.G.; at 130° F. the pounds pressure exerted by "Freon21" vapor is 50 P.S.I.G.; at 70° F. the pounds pressure exerted by "isobutane" vapor is 31 P.S.I.G.; at 130° F. the pounds pressure exerted by"iso butane" is 97 P.S.I.G.; at 70° F. the pounds pressure exerted by"Freon 12" is 70 P.S.I.G.; at 130° F. the pounds pressure exerted by"Freon 12" is 180 P.S.I.G.; at 70° F. the pounds pressure exerted by"Freon 502" is 150 P.S.I.G.; and at 130° F. the pounds pressure exertedby "Freon 502" is 350 P.S.I.G. Also assumed is that the column of waterin pipe 34 is approximately 600' high having a back pressure ofapproximately 259 P.S.I.G. Therefore, by utilizing the present system ofmultiple-stages with small temperature differentials, the liquid ismoved from a pressure of 0 P.S.I.G to the back pressure of the 600'column of water, 259 P.S.I.G.

The water in the last pumping stage is prevented from prematurelyexiting the last check valve 15 by the back pressure of the waterresiding in the output pipe 34. This pressure is dependent upon theheight in which the water is to be pumped. This back pressure holds theoutput check valve 15 closed except during the high temperature part ofthe cycle when the last stage using "Freon 502" develops a pressure of350 P.S.I.G.

In FIG. 10, liquid "A" is graphically shown as being "Freon 113", liquid"B" is graphically shown as being "Freon 11", liquid "C" is graphicallyshown as being "Freon 21", liquid "D" is graphically shown as being "isobutane", liquid "E" is graphically shown as being "Freon 12", and liquid"F" is graphically shown as being "Freon 502".

To indicate the operation of the heat-powered pump system 244, water 7in connecting means or pipe 8 at ground level would have a pressure of14.7 absolute or 0 P.S.I.G. Therefore, the water source side of checkvalve 9 would stand at 0 P.S.I.G.

Assuming that in the beginning of the cycle cold water flows throughfirst trough 42 and hot water flows through second trough 43, the coldwater in first trough 42 would cause the vapor pressure of liquid "A" tobe at -9.7 P.S.I.G. Therefore, the water 7 would flow through pipe 8 andfill pressure chamber 16. The gate control means 132 would then beactivated to change the flow of hot and cold water so that hot waterflowed through first trough 42 and cold water flowed through secondtrough 43.

The liquid "A" ("Freon 113") would then rise to a vapor pressure of 4P.S.I.G. The flexible member 23 in pumping stage 2 would be deflated andwhen the system has been operating, would have a pressure of 0 P.S.I.G.The liquid within the pumping stage 1 would then be forced by the highpressure through check valve 10 into pumping stage 2. As the systemcontinues operation, when the hot and cold water change in the troughs,the liquid will be pumped to the next highest numbered stage at a highpressure. When the water in second trough 43 is hot, liquid "B" (Freon11") would have a vapor pressure of 28 P.S.I.G. which would be greaterthan the cold vapor pressure of 10 P.S.I.G. of the liquid "C" ("Freon21") in pumping stage 3. When the hot and cold water in the troughs areagain changed, the liquid in pumping stage 3 would be subjected to avapor pressure of 50 P.S.I.G. and would flow through check valve 12 intopumping stage 4 which has liquid "D" ("iso butane") at a cold vaporpressure of 31 P.S.I.G.

When the hot and cold water in the troughs are again changed, the liquidwithin pumping stage 4 would be subjected to a vapor pressure of 97P.S.I.G. and will be forced through check valve 13 into pumping stage 5,which has liquid "E" ("Freon 12") at a cold vapor pressure of 70P.S.I.G.

When the hot and cold water in the troughs are again changed, the liquidwithin the pumping stage 5 will be subjected to a vapor pressure of 180P.S.I.G. and will be forced through check valve 14 and into pumpingstage 6, which has liquid "F" ("Freon 502") at a cold vapor pressure of150 P.S.I.G.

When the hot and cold water in the troughs are changed again, the liquidwithin pumping stage 6 will be subjected to a vapor pressure of 350P.S.I.G. and will be forced through check valve 15 and into pipe 34which has a back pressure of 259 P.S.I.G.

FIG. 10 is simply illustrative of the use of the present invention forsix specific liquids at one specific cold temperature and one specifichot temperature. The principles of the present invention may be utilizedwith any number of liquids as long as the hot vapor pressure of anygiven stage is greater than the cold vapor pressure of the next largernumbered stage. The preceding stage must always reach a higher pressurethan the subsequent stage so that the liquid will be pushed through thecheck valve into the subsequent stage.

As illustrated in FIG. 2 and FIG. 4, liquids "A", "C", and "E" are inthe same first trough 42 and are always simultaneously subjected toeither cold or hot water. Liquids "B", "E", and "F" are also in the samesecond trough 43 and are always simultaneously subjected to either coldor hot water.

FIG. 11 is a schematic representation of gate control means 132. Gatecontrol means 132 comprises a cable 50 secured to one of the containersin first trough 42 and second trough 43. Container 44 which is in firsttrough 42 is illustrated as was previously shown in FIG. 7.

Cable 50 wraps around pully 51 and is anchored in rocker bar 52 at cableanchor 60. Rocker bar 52 rotates about pin 53. A spring 54 is attachedto ground anchor 145 from movable bracket 55, which is movable on rockerbar 52. Movable bracket 55 is placed on rocker bar 52 in a manner thatthe weight of the container 44, when empty, is approximately equal theopposing force of the rocker arm mechanism together with the tension onspring 54, when spring 54 is in its contracted position. When container44 is empty, rocker bar 52 is in the lower position shown in solid linesin FIG. 11.

Magnet 56 is adjacent to lower reed switch 57 and upper reed switch 58.Lower reed switch 57 and upper reed switch 58 are magnetic proximityswitches. When the magnet 56 is positioned close to the lower reedswitch 57, a signal is sent through wire 140 to control logic mechanism59. When the magnet 56 is positioned close to the upper reed switch 58,a signal is sent through wire 139 to control logic mechanism 59.

When the vaporized liquid "A" is cooled and returned to the container44, container 44 will increase in weight due to the condensation of thevaporized liquid "A" in container 44. The weight will pull on cable 50through pully 51 and cable anchor 60, and rocker bar 52 will risecausing magnet 56 to be in proximity with upper reed switch 58 at thetime that the container 44 is approximately full. A signal is thentransmitted through wire 139 to control logic mechanism 59. Controllogic mechanism 59 would then turn off cold water pump 68 and hot waterpump 69 and energize gate motor 137 through wire 143 and gate motor 138through wire 144. The gate motors would switch the gates 62 and 65 to adifferent position where the gates will remain until the control logicmechanism 59 again receives a signal to switch the gate positions.

After the gates are switched, the pumps are again started and cold waterwould be diverted through the trough which previously had held hotwater, while hot water would be diverted through the trough thatpreviously held cold water.

When the hot water causes the liquid "A" in container 44 to vaporize tosuch an extent that container 44 becomes light to such a point that itis virtually empty, the rocker bar 52 will be lowered so that magnet 56is in proximity with lower reed switch 57 causing a signal to pass viawire 140 to control logic mechanism 59. The control logic mechanism 59would then again pass signals to the gate motors and to the pumps inorder to change the cycle of the pumps operation.

Wire 143 is connected between control logic mechanism 59 and gate motor137. Wire 144 is connected between control logic mechanism 59 and gatemotor 138. Wire 141 is connected between control logic mechanism 59 andcold water pump 68. Wire 142 is connected between control logicmechanism 59 and hot water pump 69.

Gate control means 132 is illustrative of one method of determining whenthe vaporizable liquid in a container has virtually completely vaporizedor has been virtually completely condensed back within the container.Other methods of determining that condition are within the scope of thepresent invention and can be utilized herein.

FIG. 12 is a lateral sectional view through input water diverting means147 at inlet gate 65. Connecting trough 79 connects input waterdiverting means 147 with liquid heating means 123 and hot water flowstherethrough. Connecting through 149 connects input water divertingmeans 147 to liquid cooling means 125 and cold water flows therethrough.

FIG. 12 is a sectional view at inlet gate 65. Inlet gate 62 works insimilar fashion to inlet gate 65 and has been previously explained inFIG. 4.

Inlet gate 65 has a gate pivoting shaft 197 which, upon direction by thegate control means 132, changes inlet gate 65 to either position 66 orposition 67. Position 66 is shown in FIG. 12 in solid lines. Position 67is shown in FIG. 12 in broken lines.

When inlet gate 65 is in position 66, it is stopped by gate stops 199and 200. When inlet gate 65 is in gate position 67, it is stopped bygate stops 198 and 201.

Outlet gate 62 has a gate pivoting shaft 248 which is similar to thegate pivoting shaft 197 of inlet gate 65.

FIG. 13 is a sectional view of input water diverting means 147 taken atSection 13--13 of FIG. 12. Gate motor 137 is shown in position to turngate pivot shaft 197 in order to place inlet gate 65 in either inletposition 66 or inlet position 67.

Wire 143 connects gate motor 137 to the control logic mechanism 59 ofgate control means 132.

FIG. 13 indicates that FIG. 12 can also be noted as being a sectionalview at Section 12--12 of FIG. 13.

FIG. 14 is a partial isometric view of heat collector trough 61 ofliquid heating means 123. Trough 61 has a top glazing 75 which istranslucent to allow light to enter the trough 61.

FIG. 15 is a sectional view of heat collector trough 61 of liquidheating means 123 taken at Section 15--15 of FIG. 14. Trough 61 isformed by treated wood 73 and is lined with styrofoam or othersheet-type insulation 74. The inside surface liner 76 of trough 61 whichis exposed to water may be a sheet of black polyethylene, other plasticfilm, or some other type of lining material. The top glazing 75 may be alayer of corrogated translucent fiberglass-type glazing. Top glazing 75provides visible light transmission and infrared blockage capabilitiesnecessary for efficient solar heating of the water within trough 61.

Trough 61 is part of a continuous loop system where water is circulatedand raised in temperature as it passes through the system. The liquidheating means 123 may be a solar heating trough, such as trough 61 whichextends for any desired distance in order to heat a desired volume ofwater to its desired temperature. However, the liquid heating means maybe any desired or desirable method utilizing any desired configurationof heating water or other liquids to be utilized in the heat-poweredpump system 244. Trough 61 holds heated water 195.

FIG. 16 is a cross-sectional view of cooling trough 151 which may beutilized as liquid cooling means 125. Any convenient or inexpensiveliquid cooling means desired or available may be utilized with thepresent invention.

FIG. 1 illustrates a river utilized as liquid cooling means 125, asource for the cold water. In areas where there is no such convenientwater source, another method of cooling water may be utilized, such asevaporative trough-type cooling trough 151.

Trough 151 has a frame 119 and a lining 120 which waterproofs coolingtrough 151 in the same manner that trough liner 76 waterproofed trough61. Differing from trough 61, the insulation is not utilized between theframe 119 and the lining 120.

Water 122 flows within the cooling trough 151. Above the cooling trough151 is a slanted roof 121 which is opaque and is designed to shield thewater from the suns rays. Opaque roof 121 is supported by high supportbracket 202 and lower support bracket 203. A plurality of brackets 202and 203 may be required depending upon the total length of trough 151.Support brackets 202 and 203 are designed so that air may flow below theroof 121 to promote evaporation from water 122 in the cooling trough151.

Many other types of cooling means may be utilized with the presentinvention which may be much more desirable and convenient than coolingtrough 151.

FIG. 17 is a schematic representation of heat-powered generating system245. The heat-powered generating system 245 operates on the basicprinciples herein utilizing small temperature differential multiplestages. These principles are utilized to form a heat-powered generatingsystem 245.

Liquid heating means 123 provides liquid through hot water pump 81 withmotor speed control 150 through connecting trough 79 to the input waterdiverting means 205. The input water diverting means 205 diverts the hotwater to either the first multiple-stage small temperature differentialheat-powered pump 134 or the second multiple-stage small temperaturedifferential heat-powered pump 135. The hot water is then directed intothe output water diverting means 204 where it is diverted to connectingtrough 78 and back to the liquid heating means 123.

Liquid is cooled in the liquid cooling means 125, and then passesthrough cold water pump 82, and into the input water diverting means205. The cold water passes from input water diverting means 205 intoeither the first multiple-stage small temperature differentialheat-powered pump 134 or the second multiple-stage small temperaturedifferential heat-powered pump 135. The cold water then passes into theoutput water diverting means 204. The cold water is diverted throughconnecting trough 148 back to the liquid cooling means 125.

The liquid heating means 123 and the liquid cooling means 125 simplyprovide hot and cold water to be utilized by the multiple stages withinthe heat-powered generating system 245. The heat-powered generatingsystem 245 has a working water system which is primed and whichtheoretically will not require the addition of any further water. Thisis the water which passes through the first multiple-stage smalltemperature differential heat-powered pump 134, through connector 110,and through the second multiple-stage small temperature differentialheat-powered pump 135, through connector 111, through inlet pipe 112 tothe hydraulic-to-mechanical power conversion means 115. From thehydraulic-to-mechanical power conversion means 115, the water passesthrough outlet pipe 97 to pass back to first multiple-stage smalltemperature differential heat-powered pump 134 via connector 100 or tothe second multiple-stage small temperature differential heat-poweredpump 135 via connector 101.

A gate control means 206 is similar to gate control means 132 and may beutilized to control gates within the input water diverting means 205 andthe output water diverting means 204. Control wire 209 extends from gatecontrol means 206 to input water diverting means 205. Control wire 211extends between gate control means 206 and hot water pump 81. Controlwire 212 extends between gate control means 206 and cold water pump 82.Control wire 210 extends from gate control means 206 to output waterdiverting means 204. Control wires 207 and 208 extend from the secondmultiple-stage small temperature differential heat-powered pump 135 tothe gate control means 206.

The gate control means 205 may be operated from any stage within eitherthe first multiple-stage small temperature differential heat-poweredpump 134 or the second multiple-stage small temperature differentialheat-powered pump 135.

Connector 99 is connected from inlet pipe 112 to inlet hydraulicaccumulator 113. Connector 98 extends from outlet pipe 97 to outlethydraulic accumulator 117. The hydraulic-to-mechanical power conversionmeans 115 drives a mechanical-to-electrical power conversion means 116which is connected by wire 129 to electrical load 133.

FIG. 18 is a schematically represented plan view of heat-poweredgenerating system 245. Within heat-powered generating system 245 arepumping stages 213, 214, and 215 which form the first multiple-stagesmall temperature differential heat-powered pump 134, and pumping stages216, 217, and 218 which form the second multiple-stage small temperaturedifferential heat-powered pump 135.

Pumping stage 213 has a pressure chamber 219 within which is anexpandable member 225. Pumping stage 214 has a pressure chamber 220within which is an expandable member 226. Pumping stage 215 has apressure chamber 221 within which is an expandable member 227. Pumpingstage 216 has a pressure chamber 222 within which is an expandablemember 228. Pumping stage 217 has a pressure chamber 223 within which isan expandable member 229. Pumping stage 218 has a pressure chamber 224within which is an expandable member 230.

Expandable member 225 contains vapor 231. Expandable member 226 containsvapor 232. Expandable member 227 contains vapor 233. Expandable member228 contains vapor 234. Expandable member 229 contains vapor 235.Expandable member 230 contains vapor 236.

Trough 89 holds container 92 for liquid 1, container 91 for liquid 2,and container 90 for liquid 3. Trough 93 holds container 96 for liquid1, container 95 for liquid 2, and container 94 for liquid 3.

The vapor 231 in expandable member 225 passes through pipe 237 fromcontainer 92. The vapor 232 in expandable member 226 passes through pipe241 from container 95. The vapor 233 in expandable member 227 passesthrough pipe 239 from container 90. The vapor 234 in expandable member228 passes through pipe 240 from container 96. The vapor 235 inexpandable member 229 passes through pipe 238 from container 91. Thevapor 236 in expandable member 230 passes through pipe 242 fromcontainer 94.

Pipe 240 has a flexible portion 243 which allows utilization of a formof gate control means 206.

In the operation of the heat-powered generating system 245, cold waterenters through connecting trough 149 from liquid cooling means 125. Hotwater enters from liquid heating means 123 through connecting trough 79.Inlet gate 83 is similar to inlet gate 65. Inlet gate 83 has an inletgate position 84 and an inlet gate position 85. Outlet gate 86 issimilar to outlet gate 62. Outlet gate 86 has an outlet gate position 87and an outlet gate position 88. Depending upon which position inlet gate83 and outlet gate 86 are in, either hot water or cold water will flowinto troughs 89 and 93. Whenever one of those troughs has hot water, theother will have cold water.

Arrow 175 indicates the hot water path with the gates in positions 84and 87. Arrow 176 indicates the cold water path with the gates inpositions 84 and 87. Arrow 177 indicates the hot water path with thegates in positions 85 and 88. Arrow 178 indicates the cold water pathwith the gates in positions 85 and 88. As shown by arrows 175 and 178,hot water and cold water may flow through trough sections 77 and 80during their journey through troughs 89 and 93.

FIG. 18 is taken at a position in time when hot water had been flowingthrough trough 89 and cold water had been flowing through trough 93.Liquid 1 in container 92 has vaporized and vapor 231 has enlargedexpandable member 225. Liquid 3 in container 90 has vaporized and vapor233 has enlarged expandable member 227. Liquid 2 in container 91 hasvaporized and vapor 235 has enlarged expandable member 229.

Liquid 1 in container 96 has cooled and vapor 234 has condensed reducingthe size of expandable member 228. Liquid 2 in container 95 has cooledand vapor 232 has condensed reducing the size of expandable member 226.Liquid 3 in container 94 has cooled and vapor 236 has condensed reducingthe size of expandable member 230.

The pressure in pressure chamber 219 expands greater than the pressurein pressure chamber 220, thereby opening check valve 103 which isbetween pumping stages 213 and 214. The pressure in pumping stage 214does not exceed the pressure within pumping stage 215, therefore, checkvalve 104 between pumping stages 214 and 215 remains closed. Thepressure in pumping stage 215 exceeds the pressure in container 110,thereby opening check valve 105 which is between pumping stage 215 andconnector 110. Water then flows through connector 110 and through inletpipe 112 to the hydraulic-to-mechanical power conversion means 115. Fromthe hydraulic-to-mechanical power conversion means 115, the water flowsthrough outlet pipe 97 and towards pumping stage 216 which has a lowerpressure, thereby, the pressure from the oncoming water is greater thanthe lower pressure within the pumping stage 216. Therefore, this opensthe check valve 106 between connector 101 and pumping stage 216. Thepressure within pumping stage 216 is less than the pressure withinpumping stage 217, thereby check valve 107 which is between pumpingstages 216 and 217 does not open. The pressure within pumping stage 217is greater than the pressure within pumping stage 218, thereby checkvalve 108 which is between pumping stages 217 and 218 is open, allowingthe liquid to flow from pumping stage 217 into pumping stage 218. Thepressure in pumping stage 218 is less than the water pressure withinconnector 111, thereby the check valve 109 which is between pumpingstage 218 and connector 111 is closed.

When expandable member 228 has contracted to its desired smallestamount, the gate control means 206 will automatically cause the gates toswitch to positions 85 and 88. This switch in gate positions will causehot water to flow through trough 93 and cold water to flow throughtrough 89. This change in temperature will cause the expanded expandablemembers to contract and the contracted expandable members to expand.This causes the check valve 105 to close and check valve 109 to openallowing for continuous flow of water through connector 111 to inletpipe 112 and utilizes the water that was stored within pumping stage 218while the water that was previously stored within pumping stage 215 wasbeing pumped through inlet connector 110 through inlet pipe 112.

During the transition period when the heat exchangers or containers 90,91, 92, 94, 95, and 96 are changing in temperature, the input to thehydraulic-to-mechanical power conversion means 115 could momentarilydrop. To smooth out pressure fluctuation at the input and the output ofthe turbine or hydraulic-to-mechanical power conversion means 115,hydraulic accumulator 113 and hydraulic accumulator 117 are utilized.These accumulators 113 and 117 may be tanks filled with compressed gasand a rubber bladder filled with water in communication with pipe 112.The accumulators 113 and 117 significantly reduce any momentary pressuredrop and, thereby, reduce the possibility of speed fluctuations in thehydraulic-to-mechanical power conversion means 115. Other methods ofreducing the momentary pressure drop or reducing speed variations may beused, if desired. The accumulator 113 acts to smooth the inlet pressureto the turbine or hydraulic-to-mechanical power conversion means 115.The accumulator 117 acts to smooth out the back pressure presented tothe turbine or hydraulic-to-mechanical power conversion means 115. Inlethydraulic accumulator 113 has a flexible member 114. Outlet hydraulicaccumulator 117 has a flexible member 118.

Very briefly, the heat-powered generating system 245 provides a steadyflow of water to the turbine or hydraulic-to-mechanical power conversionmeans 115 by providing a burst of water from the first multiple-stagesmall temperature differential heat-powered pump 134, followed by aburst from the second multiple-stage small temperature differentialheat-powered pump 135, followed by a burst from the first multiple-stagesmall temperature differential heat-powered pump 134, followed by aburst from the second multiple-stage small temperature differentialheat-powered pump 135, and so forth. Extending from turbine 115 is amechanical-to-electrical power conversion means 116 which is connectedto an electrical load 133 via connecting wire 129.

FIG. 19 is a graphical representation showing the relationship betweenthe pounds pressure per square inch gauge and the stage utilized withthe specific vaporizable liquid and temperature applied thereto forvarious stages in the pumping sequences within the heat-poweredgenerating system 245.

FIG. 19 is illustrative of either the first multiple-stage smalltemperature differential heat-powered pump 134 of the secondmultiple-stage small temperature differential heat-powered pump 135.However, remember that when the hot water flows through one of thetroughs 89 or 93, that cold water flows through the other trough,thereby causing the opposite condition in the various similar stages.

For the purposes of FIG. 19, the cold water temperature is assumed to be70° F. and the hot water temperature is assumed to be 130° F.

For example, utilizing liquid 1 as "Freon 12" when pumping stage 213 isat the hot vapor pressure of 180 P.S.I.G., the pumping stage 216 will beat the cold vapor pressure of 70 P.S.I.G. Utilizing "Freon 115" asliquid 2, when the pumping stage 214 is at the cold vapor pressure of110 P.S.I.G., the pumping stage 217 would be at the hot vapor pressureof 275 P.S.I.G. Utilizing "Freon 13B1" as liquid 3, when the pumpingstage 215 is at the hot vapor pressure of 429 P.S.I.G., the pumpingstage 218 would be at the cold vapor pressure of 197 P.S.I.G.

The principles of these pumping stages are the same principles aspreviously illustrated and discussed in FIG. 10. A key fact ofimportance is that the hot vapor pressure of a stage must exceed thecold vapor pressure of the next stage in order to obtain flow throughthe check valves between the stages.

Since the back pressure to the hydraulic-to-mechanical power conversionmeans 115 is equal to the input pressure on either pumping stage 213 orpumping stage 216, whichever has an open check valve and the lowerpressure, then the back pressure of the turbine orhydraulic-to-mechanical power conversion means 115 would be equalapproximately to 70 P.S.I.G. The turbine 115 has an input pressure ofapproximately 429 P.S.I.G. and, therefore, would have a pressure head ofapproximately 359 P.S.I.G. Many other liquids may be utilized in thesame or a different plurality of stages which are of similar nature andwhich conform to the criteria of the present invention.

FIG. 20 is a sectional view of check valve 13 at Section 20--20 of FIG.5. Upper hinged member 159 opens and closes upper opening 168. Middlehinged member 160 opens and closes middle opening 169. Lower hingedmember 161 opens and closes lower opening 170.

Check valves 102, 103, 104, 105, 106, 107, 108, and 109 are utilized inthe heat-powered generating system 245 and may be of similar nature tothe check valve 113 and other check valves within pump body 131 and areutilized in the same way. A plurality of hinged members may be utilizedalong with any other desired type of check valves to satisfy the desireof the user.

Each of the containers holding the various liquids is actually a heatexchanger which can be tailored in size for each pumping stage in amanner that each of the flexible members within the various pumpingstages will be properly enlarged or contracted at the proper time forthe cycle to change with the maximum efficiency and utilization of thepressure differentials. The system is designed to be in synchronization.The bladders which are filling with vapor reach their maximum at thesame time that the bladders that are contracting reach their minimum.Each of the containers may be designed as a heat exchanger to be of suchsize and to retain such qualities as a liquid-to-liquid heat exchangerso as to aid in the synchronization of the entire system.

In both the pump system and the generating system, the systems canoperate from any two sources of hot and cold water. Any desired sourceof hot and cold water can be used. A solar collector of any form can beutilized. A solar pond could be utilized under the proper circumstances.

Each different vaporizable liquid has a different vapor pressure versustemperature relationship. By selecting the correct vaporizable liquidfor the heat exchangers or containers of each stage, the hydraulicpressure caused by the heat exchanger being at the high temperature fora given even-numbered stage can be made higher than the hydraulicpressure in the subsequent odd-numbered stage when its heat exchanger isat the low temperature. Water will flow from any even-numbered stage tothe next odd-numbered stage even though the odd-numbered stage containsa vaporizable liquid with a higher vapor pressure for a giventemperature.

The first liquid, which may be water, is incrementally elevated inpressure stage-by-stage to the pressure of the last stage and then itexits the multiple-stage small temperature differential heat-poweredpump. The plurality of pump stages has the capability of utilizing thesmall temperature differential heat source to pump a liquid greatlybeyond the vapor pressure differential of a single vaporizable liquid.The output pressure of the multiple-stage small temperature differentialheat-powered pump is limited only by the high temperature vapor pressureof the vaporizable liquid used in the last stage allowing itsapplication for very high pressure requirements.

The present invention may be utilized for pumping water from a stream orother surface source to an elevated location suitable for storage ofwater. The stored water would then descend through a pipe and power aconventional hydraulic turbine electric generator combination forcommercial electric power production. The stored water may be utilizedto power the turbine at night and during intervals of low solar flux ifsolar energy were the source of heating the hot liquid for the system.The elevated location may be a reservoir and the reservoir output may beused for irrigation purposes or for hydro-electric power.

The containers may be heat exchangers of the liquid-to-liquid variety.The purpose of the heat exchangers is to transfer heat from the liquidin the trough to the liquid within the container and vice versa. Theamount of liquid within the container and the container is designed sothat when vaporized, enough gas is generated to inflate the flexiblemember to nearly the size of the pressure chamber in the pumping stage.The present invention enables generation of significant mechanical powerfrom small temperature differentials and can be utilized to takeadvantage of energy from solar collectors. This invention provides aheat operated pump which can achieve high output pressure pumpingcapacity. This invention is capable of easily converting large amountsof low temperature differential thermal energy into hydraulic horsepowerwhich can then be utilized to power a hydraulic turbine electricgenerator combination. The systems herein can offer a practical methodof converting solar energy into cheap electrical power and do much tomake solar energy a practical alternative to fossil fuels.

While the invention has been described with reference to specificembodiments, the description is illustrative and is not to be construedas limiting the scope of the invention. Various modifications andchanges may occur to those skilled in the art without departing from thespirit and scope of the invention as defined by the appended claims.

I claim:
 1. A pump system for pumping a first liquid from a source to anoutput facility comprising:a. a multiple-stage pump comprising:(1) aplurality of pumping stages; and (2) a plurality of check valves, one ofsaid plurality of check valves being located on the input and output ofsaid multiple-stage pump and between each of said plurality of pumpingstages; b. each of said plurality of pumping stages comprising:(1) apressure chamber operable to hold said first liquid; and (2) a flexiblemember within said pressure chamber operable, when expanded, to exertpressure against said first liquid and to force said first liquid fromsaid pressure chamber through the one of said plurality of check valvesbetween said pressure chamber and the next pressure chamber of the nextsubsequent pumping stage of said plurality of pumping stages or saidoutput, if said pressure chamber is within the last of said plurality ofpumping stages, when said pressure within said pressure chamber exceedsthe next pressure in said next pressure chamber or said output; c. eachof said flexible members, connected to a container which is one of aplurality of containers; and d. a plurality of vaporizable liquids, oneof said plurality of vaporizable liquids contained within each one ofsaid plurality of containers, whereby each said container holds one ofsaid plurality of vaporizable liquids and when said container issubjected to a hot temperature, said one of said plurality ofvaporizable liquids vaporizes causing said flexible member to expand andwhen said container is subjected to a cold temperature, said one of saidplurality of vaporizable liquids condenses causing said flexible memberto contract, wherein each said one of said plurality of vaporizableliquids which vaporizes into said flexible member has a higher pressure,when heated to said hot temperature, than the cold pressure of the nextsaid one of said plurality of vaporizable liquids which vaporizes intothe next flexible member within said next pressure chamber or to saidoutput, if said flexible member is within said last of said plurality ofpumping stages, wherein connected to said plurality of pumping stagesare a first heat exchanger and a second heat exchanger which utilize ahot liquid to provide said hot temperature and a cold liquid to providesaid cold temperature.
 2. A pump system according to claim 1 furthercomprising temperature alternating means operative to change thetemperature to which each said container is subjected from said hottemperature to said cold temperature and from said cold temperature tosaid hot temperature, simultaneously so that the one of said pluralityof vaporizable liquids which determines the state of each said flexiblemember within said pressure chamber of each of said plurality of pumpingstages will be at a different temperature than the one of said pluralityof vaporizable liquids which determines the state of the next saidflexible member within the next subsequent said pressure chamber of saidplurality of pumping stages.
 3. A pump system according to claim 1wherein said first heat exchanger is operative to provide said hottemperature and said cold temperature to each of said plurality ofcontainers which have said plurality of vaporizable liquids determiningthe state of each said flexible member in every odd-numbered stage ofsaid plurality of pumping stages.
 4. A pump system according to claim 3wherein said second heat exchanger is operative to provide said hottemperature and said cold temperature to each of said plurality ofcontainers which have said plurality of vaporizable liquids determiningthe state of each said flexible member in every even-numbered stage ofsaid plurality of pumping stages.
 5. A pump system according to claim 4further comprising temperature alternating means operative to change thetemperature to which each said container is subjected from said hottemperature to said cold temperature and from said cold temperature tosaid hot temperature, simultaneously so that the one of said pluralityof vaporizable liquids which determines the state of each said flexiblemember within said pressure chamber of each of said plurality of pumpingstages will be at a different temperature than the one of said pluralityof vaporizable liquids which determines the state of the next saidflexible member within the next subsequent said pressure chamber of saidplurality of pumping stages.
 6. A pump system according to claim 4wherein said first heat exchanger and said second heat exchanger utilizesolar energy to provide said hot temperature.
 7. A pump system accordingto claim 1 wherein said hot liquid is hot water and said cold liquid iscold water.